Dial indicating mechanism



May 29, 19.51 H. J. snsmANN ETAL DIAL INDICATING MECHANISM Original Filed Feb. 26, 1948 I 8 $hee1;s--She'e1'.- 1

JNVENTORS.

HAROLD J. S EKMANN GEORGE J. KASSELMAN/V l LDMMS. 3Mw- ATTORNEYS.

' H. J. SIEKMANN' ETAL May 29, 1951 DIAL INDICATING MECHANISM Original Filed Feb. 26, 1948 8 Sheets-Sheet 2 I] II' III INVENTORS. HAROLD .1. .SIEKMANN asonaz .1. KASSEL MANN ATTORNEYS.

Ifllllllllllll May 29, 1951 H. J. SIEKMANN ETAL 2,554,721

' DQIAL INDICATING MECHANISM Original Filed Feb. '26, 1948 a Sheets-Sheet :5

IN V EN TORS.

HAROLD J. S/E/(MA/VA/ GEORGE J.KASSELMAN/U A TTORNEYS.

M y 1951 H. J; SIEKMAINN ETAL I 2,554,721

DIAL INDICATING MECHANISM Original Filed Feb. 26, 1948 8 Sheets-Sheet 4 IN V EN TORS HAROLD J. S/E/(MAN/V GEORGE J. K A SSE L NA NA! ATTORNEYS.

May 29, 1951 H. J. SIEKMANN ETAL 2,554,721 DIAL INDICATING mcmuxsu I Original 'FilgdFeb. 26, 1948 8 Sheets-Sheet 5 HAROLD J. S/EKMANN GEORGEKA$SELMANN K DLWM SM ATTORNEYS.

May 29, 1951 H. J. SIEKMANN ET AL- DIAL INDICATINGMECHANISM Original Filed Feb. 26,; 1948 8 Sheets-Sheet B IN V EN TORS HAROLD J. SIEKMANN GEORGE J. KASSELMA/IMI IBIIMM A T TOR/VEYS.

May 29, 1951 H. J. SIEKMANN ETAL 2554,72 1

DIAL INDICATI'NG MECHANISM Original Filed Feb; 26, 1948 8 Sheets-Sheet 7 INVENTORS. HAROLD J. S/E/(MA/V/V GEORGE J. KASSELMAN/V KMMSM A TTORNEYS.

May 29, 1951 H. J. SIEKMANN :1- AL- DIAL INDICATING .macnmrsu Original Filed Feb. 26, 1948 8 Shasta-Sheet 8.

MOTOR HORSE POWER IN V EN TORS HAROLD J. S/EKMAN/V GEORGE J.KA.S$ELMANN iomg-m A TTORNEYS.

Patented May 29, 1951 UNITED STATES PATENT OFFICE Cincinnati, Ohio, assignors to The R. K. Le Blond Machine Tool 00., Cincinnati, Ohio, a

corporation of Delaware.

Original application February 26, 1948, Serial No. 11,274, now Patent No. 2,545,053, dated March 13, 1951'. Divided and this application April 16, 1949, Serial No. 87,886

8 Claims. 1

This invention is a divisional application of an application Serial Number 11,274, filed February 26, 1948, now Patent No. 2,545,053, dated March 13, 1951.

This invention pertains to improvements in dial indicating mechanism for machine tools and is particularly directed to dial indicating mechanism for modern type tool room lathes.

One of the objects of this invention is to provide an improved dial for controlling various speed ranges for a tool room lathe headstock transmission which is direct reading for all operative ranges selected.

Still another object of this invention is to provide a dial indicating mechanism for a lathe having a plurality of segmental series of indicia peripherally arranged on the dial together with means for selecting various ranges in the lathe headstock for automatically presenting a proper segmental scale into indicative position for any speed and range selected.

Still another object of this invention is to provide a dial indicating mechanism associated with the gear shifting control lever and the motor speed control rheostat of a lathe headstock transmission which automatically presents different segmental scales to indicative position upon manipulation of the gear shift lever for different speed ranges and which dial indicates at all times directly the operating speed of the headstock for any selected positions of the gear shift lever and rheostat control.

Still another object of this invention is to provide a dial in association with a pair of control members, one of which members moves through 360 degrees of rotation to effect its control function and the other of which rotates only through a partial revolution to effect its control function, said dial having inter-related transmission means for positioning a series of segmental indi= eating dials to indicative position relative to a movable indicating mark so as to provide a direct reading dial for any position selected for said control members.

Further features and advantages of this invention will appear from detailed description of the drawings in which:

Figure 1 is a view in front elevation with parts broken away to show the arrangement of certain electrical instrumentalities of a lathe including transmission and control mechanism designed in accordance with the precepts of this invention.

Figure 2 is a view in front elevation of the 2 headstock and on an enlarged scale as compared to Figure 1.

Figure 3 is an enlarged detailed view of the gear shift lever and dial associated therewith.

Figure 4 is a view taken as a vertical section normal to the spindle. This view is taken about on the plane represented by the line 44 of Figure 2.

Figure 5 is another vertical section taken normal to the axis of the spindle and is taken about on the plane represented by the line 55 of Figures 1 and 6.

Figure 6 is a compound sectional view developing the various operating axes and is taken about on the planes represented by the lines 66 of Figure 5.

Figure 7 is an enlarged detailed view, partly in section and partly in elevation, of the connections between the control mechanism and the rheostat at the rear of the head. This view is taken about on the plane represented by the line 1-'l of Figures 8 and 9.

Figure 8 is an enlarged detailed sectional view taken about on the plane represented by the line 8-8 of Figure 7.

Figure 9 is another enlarged detailed sectional view taken about on the plane represented by the line 9-3 of Figure 7.

Figure 10 is a detailed view taken from the rear of the head with the casing removed and showing in detail a part of the interlock which prevents the gears being shifted until the rheostat is adjusted to low speed. This view is taken about on the plane represented by the line I0'l0 of Figure 11.

Figure 11 is a detailed horizontal section being taken about on the plane represented by the line Il-l i of Figure 10.

Figure 12 is a detailed plan view on an enlarged scale of a certain part of the gear shifting mechanism.

Figure 13 is an enlarged fragmentary sectional View taken on the line l3-l3 of Figures 3, 14, and 15 showing the dial pointer and associated operating instrumentalities.

Figure 14 is an enlarged sectional view of the indicator mechanism being taken on the plane represented by' the line ill-I4 of Figure 13.

Figure 15 is an enlarged sectional view taken normal to the axis of the operating shaft and is taken about on the plane represented by the line I5-l5 of Figure 13.

Figure 16 is an enlarged detailed plan view showing the shifting mechanism for changing the drive to the feed for coarse thread. cutting.

Figure 17 is a graphical illustration showin the power output over the operating range provided by the motor and transmission hereof.

General arrangement Figure 1 illustrates a lathe which may be typical of the type to which the present invention is adapted. Such a lathe comprises a bed 20 which is supported by legs 2| and 22, the leg 2| being located at the tailstock end and'the leg 22 at the headstock. Upstanding from the bed 20 is the tailstock which is referred to generally as 23 while from the opposite end upstands the headstock 24.

An apron 25 is shown as being positioned intermediate the headstock 24 and tailstock 23 and this apron carries a cross slide 26 which in turn carries a tool post represented at 2'5. The above noted elements are common to all lathes and are described purely for the purposes of indicating the environment of the present invention.

Below the bed 20 there is a motor generator set which is shown in broken lines in Figure l and which is designated 2 la. The motor of this set is adapted to take current from an A. C. source of supply which is convenient to the lathe. As a practical matter, such a source of supply will most likely be a three phase, 60 cycle current under a voltage of either 226 or 440 volts as that is the type of current most commonly available around the places where lathes of this type are used. The motor of the unit 2 la drives the generator which provides current for a main driving motor represented at 22a. This motor 22a is a variable speed direct current motor. The panel represented at 20a is shown as being adapted to carry various electrical devices which are used in conjunction with the unit 2m and motor 22a. The various elements and make up of the electrical equipment itself is not a part of the present invention because it is purchasable as such from any of the various manufacturers of electrical equipment of this type. The only thing with which the present invention is concerned is that the motor 22a may be adjusted to provide varying speeds in its output shaft and this is accomplished under an arrangement in which the voltage of the armature circuit is varied. However, the invention is not to be limited in this respect as the variable speed on the part of the motor 22a could be provided for in other ways. Moreover, the design of the motor 22a itself is not a part of this invention as it is purchased as such from a manufacturer of electrical equipment.

The center of the work spindle is shown at 240 in Figure 1 while the spindle itself is indicated at 24a in Figure 6. This spindle 24a carries the usual work fixture indicated at 242) and shown in both Figures 1 and 6. The motor 22a has an output or drive shaft 221) and the spindle 24a is driven from this shaft 2212. Upon referring to Figure 4 it will be noted that the motor shaft 221) drivably carries a pulley 220, the driving relation being established by a key 22d. A back gear shaft 28 (see Figures 4 and 6) drivably carries a pulley 28a, the driving relation being established by the key shown at 29 and the spindle 240. carries a pulley 36 which in some conditions is journaled for free rotation about the spindle and in other conditions is clutched thereto. Belts 3! pass over the pulleys 220, 23a, and 35 and guide roll 32 in the manner shown in Figure 4 and these belts serve to transmit the power forrotat-ing the splndle 24a. This same setup also-providt v mg power for operating the fine tool feed as will be later described.

Transmission The transmission of this invention is intended to provide three speed ranges. The highest of these ranges is the direct belt drive from the motor shaft 22b to the spindle 24a and is accomplished by clutching the pulley 36 to the spindle 24a while the other gears are ineffective. The intermediate speed range is provided by the high back gear drive and the lowest range by the low back gear drive.

As shown in Figure 6, the pulley is journaled on the spindle 24a by bearing assemblies 33. A clutch member 34 is journaled in a wall of the headstock such as represented at by bearing assemblies 36. This clutch member 34 is keyed to the spindle 24a by the key shown at 31. The clutch member 34 carries a plurality of pins, one of which is shown at 33, and which pins are slidable in the clutch member in a direction parallel to the axis of the spindle. Each of the pins 38 has a head at 39 which provides for its connection to a shifting collar 49 that is slidable on the spindle 24a. The collar 40 has a groove 4| which receives the opposite ends of a shifting yoke that is shown at 42 in Figure 5. The ends of the pins 38 remote from the heads 39 take the form of points which are adapted to be received in openings formed in a plate 43 that is drivably carried by the pulley 35. Thus, when the pins 38 engage the openings in the plate 43 the driving relation between the pulley 36 and spindle 24a is established. On the other hand, when the pins are disengaged from these openings, the pulley 36 is free to rotate about the spindle.

Positioned between the back gear shaft 28 and the spindle 24a are a pair of aligned shafts 44 and 45. The shaft 44 has its outer end journaled in the wall 35 by a bearing assembly shown at 45. The inner end of the shaft 44 is journaled in a bearing 47 carried by a wall 48 formed in the headstock 24. The shaft has its inner end journaled in a bearing 49 carried in the wall 49 and its outer end journaled in a bearing 56 car-- ried by the wall 48a of the headstock 24.

A compound gear 5! carrying a gear 52 at one end and a pinion 53 at the other is slidable on the shaft 45 and is keyed thereto by the key shown at 54. In one position of the compound gear 5| the pinion 53 is adapted to mesh with a gear 55 that is keyed to the spindle 2411 as shown at 56. The gear 52 meshes with a pinion 5'! that is keyed to a sleeve 58 that is journaled on the back gear shaft 28. It is notable that this engagement of the gear 52 and pinion 51' takes place in all positions of the compound gear 5i. The back gear shaft 28 is journaled in the headstock wall 35 by the bearing shown at 59 and 60. A part of this shaft 28 is splined as shown at 6| and slidably mounted on this splined part is a gear 62. This gear 62 has an extension formed with a groove 63 which receives one end of a shifting arm that is shown in broken lines in Figure 5 at 64 and also in Figure 12. A pinion 65 is keyed to the shaft 44 as indicated at 66 and this pinion is slidable on the shaft. A gear 61 is in turn keyed to the pinion 55 as shown at 68 and is movable on the shaft 44. The unit comprising pinion 65 and gear 61 is adapted to be shifted longitudinally on the shaft 44 by a shifting member shown at 69 in Figures 5 and 12. The member 69 is formed with a slot which receives the gear 61 and is carried at one end of an arm 10.

The sleeve 58 which, it will be recalled, is jour- 5. naled onthe back gear shaft 28, thebearingsibe ing: shown at H, carries. at its. forward end an external gear 12 and an internal gear 13. The internal gear 13- is adapted. to mesh with the pinion 62 while the external gear 7 2 is adapted to mesh with the pinion 65.

Before describing the manner in which the shifting of the several gears is accomplished,v it is noted that when the pinion 62 meshes with the internal bear l3 and the pinion 53' is engaged with the gear 55, the drive is from the pulley 28a through the shaft 28, gears 62 and 1.3, sleeve 58 pinion 51, gear 52 of the compound gear pinion 53, and gear 55 to the spindle 2%.. Under this condition, the pulley so is, of course, not clutched to the spindle 24a but merely journals freely thereabout. This is the intermediate range or high back gear speed.

In low back gear, the pinion 53 and gear 55 are still engaged by the gear 62 is shifted so that it engages the gear 67 rather than the internal. gear 13. At the same time, the unit made up of pinion 65 and gear 61 is shifted so that the pinion. 65 meshes with the gear 12. The drive is now from pulley 28a through shaft 28, gear 62, gear 61-, pinion B5, gear 72, sleeve 58, pinion 5?, gear 52 of the compound gear 5|, pinion 53,. and gear 55' to the spindle 24a.

Shifting mechanism Upon referring to Figure 5 it will be noted that a sleeve 14 is journaled in. the upper part of the headstock 24 in a direction transverse to the axis of the spindle 24a. A gear shift lever 15 is drivably connected to this sleeve in a manner to be later described. The important thing for the moment is that swinging of the lever causes rotation of the sleeve 14 to shift the gears and clutches so as to render any range desirable effective.

As above explained, the yoke 42 engages the groove 4| of the shift ring Ml. This yoke 2 is carried by a sleeve 16 that is slidable on a rod 11 mounted below the sleeve M and in a direction transverse thereof. A ring 78 is drivably carried by the sleeve 14 and has gear teeth. as indicated at 19 which engage complemental teeth. on the sleeve 16. Thus, as the sleeve it is rotated the ring I8 is rotated and the engagement of the teeth 19 with the sleeve it causes the latter to slide along the rod TI and impart a corresponding rectilineal movement to the yoke 42. This arrangement is quite similar to that described in the patent to Groene No. 2,419,639.

Slidable on a rod Bil that is positioned below the sleeve l4 and which extends in a direction transverse thereof is a shifting member 8! that is formed with a slot which receives the gear 52. A ring 82 is drivably mounted on the sleeve M and has teeth at 355 which engage complemental teeth on the member 8i. Thus, as the sleeve '54 is rotated, the ring 82 is rotated and the teeth 83 cause the member 8| to slide along the rod 8! As the gear 52 is engaged by this member 8|, a corresponding movement is imparted thereto.

Referring now more particularly to Figure 12 which will be considered in conjunction with Figure 5, it will be noted that the sleeve 14 drivably carries a ring 84 which has formed in it a cam slot 35. A roller 86 is received in this cam slot 85 and is carried on a pin 8'! which is in turn carried by an arm 88. The end of the arm 8!! remote from the roller 86 is drivably connected to a vertically extending shaft 39. Thus, as the ring 8G is rotated, the cam slot 85 affects the roller 85 to cause a swinging of the arm 88 about the shaft 89 as an axis. It will be recalled that the arm 10 carries the member 69 which is formed with. a slot that receives the gear 67. This arm 10 is also drivably connected to the shaft 89. The arm 64 is also drivably connected to the shaft. 89 and at its free end carries a shoe 99 which is received in the groove 63. It is therefore evident that as the sleeve 74 is rotated the cam ring 84 and arm 83' impart a corresponding rotating motion to the vertical shaft 89. This causes a rocking. of the arms 65 and 19 to move the gear 62 in one direction and the gear 6! in the opposite direction. Thus, when the gear 62 is moved into mesh with the internal gear 13, the unit made-up of pinion 65 and gear 61 is moved in the opposite direction causing the pinion 65 to become entirely free and clear of the external gear I2. Then again, when the pinion 62 is shifted into engagement with the gear til, the latter moves as a unit with the pinion 55 to cause the pinion 65 to mesh with the gear 132.

Control and indicating mechanism It will be noted from Figure 5 that the sleeve 14 enclosesv a shaft 9!. Both the sleeve 14 and shaft 9| extend substantially across the headstock at the top. The mechanism and arrangement at the rear of the headstock is shown in Figures 7 to 1 inclusive. Upon referring to Figure '7 it will be seen that a rheostat is represented at 92. It is this rheostat that controls the speed at which the motor 22a operates. Extending inwardly from the rheostat 92 is a control shaft 93. Drivably carried by the shaft 93 is a gear 94 with which meshes an idler gear 95. A second gear as meshes with the idler gear 95 and is drivably carried by the shaft 9|. At this point, it is well to note that the gears 94 and 96 are of substantially the same diametrical dimensions so as to provide for a l to 1 ratio between the shaft 9| and rheostat control shaft 93. A disc 91 is formed with a central opening which receives a thimble 93 with the thimble in turn receiving the shaft 9!. This disc 97 is held against rotation by a pin 99 which is screwed into the headstock framework 35 as indicated at Hill. The end of the pin 99 is received in a notch shown at llll in Figure 9.

This disc 9! is formed with three openings H12, H13, and [64. Any of these openings is adapted to receive the head Hill of a pin E06 which is carried by a disc lel that is keyed to the sleeve 14 as indicated at E88. It is evident that when the head N35 is received in any of the openings I02, I03, or Hi4, the sleeve it cannot be rotated. Thus, when this engagement is maintained there can be no shift in the transmission from one speed range to another. In order to permit such a change, it is necessary that the shaft 8! be moved laterally within the sleeve it so as to move the disc fill away from the pin me. This may be accomplished by the operator pressing against the button shown at we providing the rheostat 92 has been adjusted to low speed.

It will be noted that the gear 9f which is pinned to the thimble 98 and shaft 95 by the pin shown at H9 is formed with a socket ill. The framework 35 carries a panel 5 i2 and extending inwardly from this panel is a pin N3, the free end of which is positioned. in close proximity to the face of the gear 95. Thus the only position in which the shaft 93 and. gear 36 which is carried thereby may be moved inwardly is when the pin H3 aligns with the socket H i. This condition of alignment obtains only when the rheostat 92 is adjusted to low speed as determined by the posi-- tion of the rear 96.

It will be noted that the shaft 9I has a reduced end portion I I4 and the end portion of the latter is slidably received in an opening H5 formed in the panel H2. An expansion coil spring H6 is disposed about this reduced portion I I4 and bears against the larger part of the shaft 9| at one end and the panel I I2 at the other. This spring normally urges the shaft 9I forwardly in the position depicted in Figure 7. However, it may be pressed rearwardly against the influence of this spring providing the pin H3 and socket III align. Briefly summing up the relation of the several interlock elements above described, it is noted that the gear shift lever I5 cannot be moved to shift gears unless the disc 91 is withdrawn from the head I05 of the pin I06. That is, there cannot be a shift in the gear ratio without first pressing against the button I09. But the latter operation is not possible of attainment until the rheostat 92 has been adjusted to low speed so as to cause the pin H3 and socket II I to come into alignment.

Referring now more particularly to Figure 13 it will be noted that the shaft 9I extends beyond the end of the sleeve I4 and is formed with a reduced portion II I on which the button I09 is pinned and thereby drivably connected thereto. This button is formed with a cup-shaped recess II 8 that receives the end of the sleeve I4 and accommodates relative movement between these parts. Drivably connected to the button I09 is a sleeve I I9 having an inner portion that is counterbored to provide a thickened portion I that rotates about another sleeve I2I held in place by a nut I22 which is threaded on the end portion of the sleeve I4.

An operating member I23 is pinned to the sleeve I I9 as shown at I24 and presents a knurled ring or knob I25 for the convenient grip of the operator. The sleeve I20 is formed with external gear teeth I26 which provide in effect a gear that is drivably connected to the knurled operating ring I25. A stationary part which is connected to the headstock 24 and which is designated I20a carries a compound gear I2I. One end of the compound gear I2'I takes the form of a pinion I 28 that meshes with the gear I25 while the other end takes the form of a pinion I29 that meshes with a reversing pinion I29a (see Figure 14) which in turn meshes with an internal ring gear I30 formed as a part of an indicating ring I3I. The latter is formed with a lip I32 that overlies the stationary part I20a. At an appropriate point on the outer periphery of the ring I3I, it is provided with a line or pointer designated I 33.

Thus, it is evident that as the ring I25 is rotated, the shaft is turned and the rheostat 92 adjusted with a 1 to 1 ratio obtaining between the control shaft 93 of the rheostat and the operating ring I25. However, due to the gear reduction provided by gears I26, I28, I29, I29a, and I30, the ring I3I is driven at a 1 to 3 ratio, that is, it only moves through one-third of the angular distance through which the ring I25 is turned. This will become important for a matter now to be described.

The gear shift handle I5 has a reduced end which is received in a socket formed in a ring I34. The latter is keyed to the sleeve I4 as shown at I35 so that as the handle 15 is swung the sleeve I4 is rotated. A circular plate I36 is anchored to the framework of the headstock by screw bolts shown at I31. A stationary gear I38 is in turn secured to the outer face of the plate I38 by-pins shown at I39. Meshing withthe gear I33 is a gear I40 that is formed integrally with a stud I 4| which is journaled in the ring I34. This stud I 4| has a reduced end I42 to which is drivably connected, as by a pin I43, a gear I44. The gear I44 meshes with another gear I45 that is carried on a sleeve I46.

A dial I4'I is drivably connected to this sleeve I46 by the pins shown at I48. Thus, as the gear lever I5 is swung not only is the sleeve I4 rotated but through the gears I38 and I40, stud I4I, gears I44 and I45, and sleeve I40 the indicating dial I41 is turned and the rate of rotation is stepped up by the gearing. Under practical conditions, the gear shift lever I5 is swung through only about degrees from either side of the vertical position depicted in Figure 3. It is necessary that this amount of movement be effective to bring either of the three sections of the dial into the uppermost position, hence this stepped up gearing.

Upon referring to Figure 3, it will be noted that the dial I4! is divided into three sections. One of these is designated belt drive and when the spindle 24a is driven directly from the belt 3I the section so designated should be in the uppermost position. The high gear position is shown at the top in Figure 3 and it is this section which cooperates with the pointer I33 when the high back gear ratio obtains. The low gear section is the lowest speed provided for and it is this section that should be at the top when the low back gear ratio obtains. It is evident that when the lever I5 is swung to accomplish the gear shift the dial I41 is correspondingly moved to bring the proper section of degrees to the top or uppermost position in which it cooperates with the pointer I 33.

It will be noted that the stationary part I200: is carried by a pin I49 that extends from the headstock 24 out through aligned slots I50 in the ring I34 and dial I4'I.

Drive to tool feed for coarse thread cutting In order to provide for the proper drive to the tool feed depending on the nature of the work, three separate drives to the tool feed are included in the lathe. One of these is the drive for fine tool feed and is effective only when the transmission is adjusted for the high speed operation of the spindle that is established when the direct belt drive is effective. The second drive is for regular thread cutting and its operation may be established when the transmission is in either of the back gear drives. The third drive to the tool feed is for coarse thread cutting and may be established only when the transmission is adjusted to render the low back gear drive effective.

Upon referring to Figure 4, it will be seen that a shaft I5I has drivably mounted thereon a pulley I52. Another pulley I53 is keyed to the back gear shaft 28. A belt I54 passes over the pulleys I52 and I53 and serves to drive the shaft I5I. This shaft I5I is shown in Figure 6 and is eifective to provide the fine tool feed in the manner described in the above identified Groene patent. Inasmuch as there is no change in this drive from the shaft I5I to the tool feed gear which is shown at I55, it is not thought necessary to here unduly lengthen this specification by repeating this descriptive matter. The Groene patent is referred to for the manner in which this is carried out. As above pointed out, this fine tool feed is effective only when the spindle 24a is in direct belt drive.

Certain gear mechanism is provided for estab:

fishing a drive from the spindle 24a to the tool feed and which drive may obtain when the transmission is in either of the back gear ratios. This gear mechanism also is adjustableto provide another drive for coarse thread cutting which is effective only when the transmissionis in-low back gear drive. This is accomplished by the mechanism now to be described. A sleeve I56'is keyed to the spindle Ma by the key shown at I51 and is slidable thereon due to presence of the elongated key'way. This sleeve :55 is formed with a groove at I58 that receives a shifting member. One end of this sleeve Is carries a gear I59 while the other end carries a gear I55.

A selector shaft IBI that is splined'is shown as being journaled in a wall of the headstock. This shaft I5! includes a part at I52 that is free from splines and rotatably mounted on this portion IE2 is a compound gear E63 providing a gear I64 and a smaller gear I65. The gear I54 meshes with a pinion I65 that is keyed to the shaft I5I. The gear I55 is adapted to be either engaged or disengaged from an internal gear I51 that is formed on a sleeve I63. The latter is also formed with external gears I69 and H5. The sleeve I68 is also formed with a groove .III which receives a shifting yoke at the end of an arm I'i'B which is actuated from the sleeve 1 It is evident that when the sleeve I53 is shifted to the left, speaking with reference to the showing of Figure 6, the internalgear E51 and the gear I55 are enga ed. At the same time, the gear I15 is disengaged from the gear we and the ears I59 and I68 are also out of mesh. The drive is therefore from the shaft l5| th ou pinion 1.5 ear I64, compound sear i s. a 5, and internal gear I57, and gear I59 to the gear atilfz which may be taken as the start of the .clri-ve to the tool feed. This is the line tool feed which is established when the spindle 2 3a is in direct belt drive.

When'the sleeve 168 is shifted to the right, speaking with reference to the showing of Fig- .ure 6, two things take place. The internal gear I16? is disengaged from the gear I65, thereby breaking or interrupting the drive from the shaft I5 i. As the movement is continued, the ear I69 engages the gear E55, thereby driving the tool feed'from the spindle 24a. This condition is intended for the cutting of regular threads and'is effective when the transmission is in either of the back gear drives. Thus, when the spindle 24a is driven either at its intermediate speed which is established by the regular back gear or at its lowest speed which is established by low back gear, the spindle 24a is driven by gears 55, 53, and 52 and the spindle in turn drives the tool feed through gears I59 and I69 which "latter gear meshes with the gear H2.

In establishing the drive to the tool feed for ,a coarse thread cutting, the sleeve I56 which carries a gear Ito is moved to the left, speaking with reference to the showing of Figure 6. It -is to be remembered that this drive is to obtain only when the transmission is in low back' gear for the spindle. In such a condition, the gear 52 will have been shifted to the right. Thus the gears 52 and ISB approach each other so as-to bring them into mesh. The gear I60 idles on the sleeve I56 and is driven directly from the gear 52. This same movement which brings the gear I 56 into mesh with the gear ,52 also brings it into meshing engagementwith the gear ,Ii'ifl. The latter being integrally formed on the sleeve L68 .dljiyesthe gear I59 which meshes with the gear I12 which is taken as the start of the tool feed.

it is evident that as the gear shift lever I5 is turned the sleeve I l-is turned and a ring I13 which is drivably carried thereby is rotated. This ring is formed with gear teeth at I" that engage a sleeve I15 which carries the yoke I16. The sleeve H5 is slidable on a shaft H1. Thus, as the gear shift lever 15 is shifted, the yoke I16, which isreceived in the groove I'lI, shifts the sleeve I15 and gear elements carried thereby. Thus, whether the drive to -the tool feed. takes its power from the shaft I5I or the spindle 24a depends on the speed range which is effective. Thus, when the direct belt drive is effective, the drive to the tool feed is from the shaft I5I but 'when-thebaci; gear ratios are obtained it is from either the spindle 24a or the gear 52. In order to shift the sleeve I 56 to vary the ratio in-this drive from the spindle to the tool feed, the-following mechanism is employed. Slidably positioned on the rod f-l' is a sleeve I-'I 8 from which depends an arm carrying a yoke that engages the groove E58. Connected to this sleeve I='I8-is a link I15 which at its other end is connected-to an arm E that extends from a hub member I8! that is-keyed to a stub shaft I82. This stub shaft m2 is-journaled in the framework and at its forward end carries a nut 1-8-3 and a "pointer I84. When the adjustment is to be made for coarse thread cutting, a wrench is applied to the nut I83 to rotate the stub shaft 8-2. This swings the arm I80, which motion is transmitted through the link I19 to shift the sleeve H8 and yoke which-is attached thereto. As the latter is positioned in the groove I58, the sleeve I58 is shifted.

Operational advantages It is possible and entirely practical to obtain from the manufacturers of electric motors a variable speed direct current motor such as-represented at 220: which will develop its basic horsepower over 7-5 percent of its range. This means that the horsepower fallsofif over the first 25 percent of the speed range. As the lathe is set up to operate at a minimum .of 6B. P..M., at this point 3 horsepoyveris developed. .-Ihis horse.- .power gradually increases up to 15 R. P. whereupon the basic horsepower ,of the motor, which is 7 horsepower, is developed and this condition obtains throughout the remainder .of the range up to '60 R. ;P. M.

The foregoing conditions obtain when the low back gear drive is effective and causes a .-25,to 1 gear reduction. --When the shift to the high back gear drive is made, the gear ratio is changed to -.;5 to =1. There is ,a slight gap between60 R.. P. M.

and {7 5 RsP. M. provided by the highhackgear at which the developed horsepower falls of)? slightly to a-minirnum of 6 'horsepoWerHbut-for all practioa-fpurposes this is taken .care of by the motor which, under practical. conditions will develop sufficient excess horsepower to accommodatethis Thus, under" conditions of actual usage,

t-here is little, if ammo-falling off ofthe horsepower in bridging the change from low back gear speed to highgear speed. i 1

This speed range' provides for revolutions of GO-R. P. M. .to 300 R. P. M. When the change is made vto the beltrd-riva the ratio is nowl to-"El and the speed range-is 300 to 1500 M. Again there is a small gapbetweeri 300-and 3f-7-5 R. P.--M. at whioh thehorsepower' m ayfall off slightly-but 'foiuall-practical purposes-this is negligible.

#It is therefore evident that \vlth the mecha- .nism above described it is possible to drive the spindle of the lathe over a speed range of from 15 R. P. M. to 1500 R. P. M. and develop substantially the basic horsepower of the motor over the entire range. There is a reduction in the horsepower from 6 R. P. M. to 15 R. P. M. and perhaps some slight reduction at the gaps indicated.

Further definite advantages are presented by the interlock mechanism. It is impossible to shift the gears without first depressing the button I09 to shift the shaft 91 but this latter action cannot take place until the rheostat 92 has been adjusted to low speed.

By providing for a gear reduction between the operating ring 125 and the pointer 133, it is possible to maintain a 1 to 1 ratio between the ring I and the rheostat control shaft 93 and yet have the pointer I33 move over an entire range of only 120 degrees. Furthermore, by providing the step up gearing between the gear shift lever '55 and the dial 141 movement of the gear shift lever is restricted to about 85 degrees to each side of the vertical position illustrated while the dial is rotated sufficiently far to bring the correct section to the uppermost position where it cooperates with the pointer I33 to indicate the speed at which the spindle is being driven.

While a preferred specific embodiment of the invention is hereinbefore set forth, it is to be clearly understood that the invention is not to be limited to the exact mechanism, devices, apparatus, speeds, and horsepower illustrated and described because various modifications of these details may be provided in putting the inven- I tion into practice within the purview of the appended claims.

Having thus fully set forth and described this invention, what is claimed is:

1. In a lathe including a work spindle to be driven, a variable speed electric motor, a rheostat associated with said motor to control the speed thereof, and a transmission adapted to operatively connect said motor to said work spindle and providing three speed ranges, a gear shift lever operatively connected to said transmission for causing a change in the effective speed range thereof, a three section dial operatively connected to said gear shift lever, a ring carrying a pointer that is adapted to cooperate with the section of said dial which is in a predetermined position, a rotatably mounted shaft operatively connected to said rheostat, an operating member for said shaft, and a reduction gear train operatively connecting said operating member to said ring.

2. In a lathe including a work spindle to be driven, a variable speed electric motor, a rheostat associated with said motor to control the speed thereof, and a transmission adapted to operatively connect said motor to said work spindle and providing three speed ranges, a gear shift lever operatively connected to said transmission for causing a change in the effective speed range thereof, a three section dial any section of which is adapted to assume an uppermost position which is the effective dial position, step up gearing between said gear shift lever and said dial whereby a certain amount of angular movement on the part of said gear shift lever causes a greater amount of angular movement on the part of said dial, a ring carrying a pointer that is adapted to cooperate with the section of said dial in the uppermost position, a rotatably .mounted shaft operatively connected to said rheostat, an operating member for said shaft, and a reduction gear train operatively connecting said operating member to said ring.

3. In a lathe, a transmission providing three operating speed ranges, a gear shift lever arranged to swing in a vertical plane and operatively connected to said transmission for causing a change in the effective speed range thereof, a three section dial, each section of said dial corresponding to one speed range of said transmission, operative connections between said dial and said gear shift lever whereby swinging of said gear shift lever causes rotation of said dial at a differentially faster rate than said lever, and a pointer cooperating with the dial section located in a predetermined fixed position.

4. In a lathe, a transmission providing three operating speed ranges, a gear shift lever operatively connected to said transmission for causing a change in the effective speed range thereof, a three section dial, each section of said dial corresponding to one speed range of said transmission, step up gearing between said lever and said dial whereby a certain amount of angular movement on the part of said lever causes a greater amount of angular movement of said dial, and a pointer for cooperating with the section of said dial which is in a predetermined position.

5. In a dial indicating mechanism for use with a lathe control having a knurled knob rotatable through a complete revolution and a gear shift lever movable to a plurality of predetermined positions through a partial revolution to effect the respective control functions of said knob and lever, a rotatable ring, an indicating pointer on said ring, a step-down transmission between said knurled knob and said ring, a rotatable dial, a series of segmental groups of dial indications circumferentially spaced around said dial associated with said pointer and corresponding to the shifted positions of said gear shift lever, a speedup transmission between said gear shift lever and said dial, said dial and pointer directly indicating the condition of control established for any position of said knurled knob and said gear shift lever.

6. In a dial indicating mechanism for a lathe having a headstock, a gear shift lever journaled on said headstock for swinging movement to three shiftable positions, a dial journaled on said headstock, three segmental series of graduations circumferentially spaced about said dial, differential speed-up gearing interconnected between said headstock and said lever to cause said lever when operated to rotate said dial a greater distance than the swinging movement of said lever, a control knob journaled on said headstock, a ring journaled on said headstock having an indicating pointer thereon indicatively positioned relative to the graduations on said dial, and a step-down transmission interacting between said headstock and said ring to cause said knob when rotated to rotate said ring and pointer a lesser amount.

'7. In a dial indicating mechanism having a lever swingable about an axis to a plurality of predetermined shiftable positions, an indicating dial rotatable about said axis, speed-up gearing interconnected between said lever and dial so that movement of said lever effects greater angular movement of said dial than the angular movement of said lever about said axis, a series of segmental dial indications corresponding to the shifted positions of said lever circumferen- 13 tially spaced around said dial, a control knob rotatable on said axis, a ring rotatable on said axis, a pointer on said ring indicatively associated with said indications on said dial, and stepdown gearing interconnected between said knob and said ring so that rotation of said knob effects a lesser amount of rotation in said ring.

8. In a dial indicating mechanism having a lever swingable about an axis to a plurality of predetermined shiftable positions, an indicating dial rotatable about said axis, speed-up gearing interconnected between said lever and 'dial so that movement of said lever efiects greater angular movement of said dial than the angular movement of said lever about said axis,1a series of segmental dial indications corresponding to the shifted positions of said lever circumferentially spaced about said dial, a control knob rotatable on said axis, a ring rotatable on said axis, a pointer on said ring indicatively 'associated with said indications on said dial, and stepdown gearing interconnected between said knob and said ring so that rotation of said knob effects a lesser amount of rotation in said ring," and a push button coaxially positioned on said axis inside of said dial, ring, and knob operable to release said lever for swinging movement.-

HAROLD J. SIEKMANN. GEORGE J. KASSELMANN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 520,280 Whittingham May 22, 1894 728,814 Whittingham May 19, 1903 1,021,875 Libby Apr. 2, 1912 1,527,247 Bouillon Feb. 24, 1925 1,563,546 Bouillon Dec. 1, 1925 1,588,004 Blood June 8, 1926 1,685,440 Tanner Sept. 25, 1928 1,985,017 Bush Dec. 18, 1934 2,331,854 Stout Oct. 12, 1943 2,331,695 Johnson Oct. 12, 1943 2,338,121 LeBlond et a1. Jan. 4, 1944 2,419,639 Groene Apr. 29, 1947 FOREIGN PATENTS Number Country Date 268,456 Great Britain Jan. 1926 

